CN101878378B

CN101878378B - Annular disk brake and method of increasing a brake pad clamping force

Info

Publication number: CN101878378B
Application number: CN200880118068.2A
Authority: CN
Inventors: A·康斯坦斯
Original assignee: Asteria Performance Inc
Current assignee: Astria Performance International Ltd
Priority date: 2007-11-27
Filing date: 2008-11-27
Publication date: 2014-01-29
Anticipated expiration: 2028-11-27
Also published as: BRPI0820398B1; KR20100095540A; SI2212580T1; EP2212580B1; PL2212580T3; EP2212580A4; PT2212580E; EP2212580A1; US8657080B2; MX2010005729A; RU2010119527A; ES2386598T3; US20100258387A1; RU2477398C2; CN101878378A; WO2009067801A1; CA2703557C; CA2703557A1; BRPI0820398A2

Abstract

The annular disk brake (10) comprises a rotor disk (60) and at least one brake pad (62, 64) arranged on each side of the rotor disk (60). The brake pad or pads (64) on one side are connected to a substantially axially-guided brake pad carrier (66). The brake (10) has a force transmitting arrangement creating a force increasing amplification between an axially-actuated member (48) and the carrier (66). This arrangement can increase the brake compactness and provide an even distribution the braking force around the circumference of the rotor disk (60). A method of increasing a brake pad clamping force is also disclosed.

Description

Annular disk brake and the method that increases brake pad clamping force

Technical field

The method that the art relates to annular disk brake and increase brake pad clamping force in annular disk brake.

Background

In the reference paper formerly having, annular disk brake is called as full-contact annular disk brake sometimes.An annular disk brake comprises at least one rotor disk, and this rotor disk is axially movable with respect to fixing parts.Rotor disk and a rotatable member (for example wheel of vehicle) are among the engaging of transfer of torque.Rotor disk is positioned between the one or more fixing brake shoe of a side and the one or more axially movable brake shoe of the opposite side of rotor disk in the axial direction.This is organized movably brake shoe and for example, is pushed against in the axial direction in the respective side of rotor disk by a starter (, pneumatic type, hydraulic type or motor starter).When these are fixing and movably these sides of brake shoe and rotor disk are in a kind of pinch engagement, drag friction and heat have been produced.

In the design of annular disk brake, exist numerous challenges.The first is wanted to produce a suitable clamping force with a starter, this starter can be assemblied in can the space for break within.Annular disk brake is often provided in vehicle, and these annular disk brakes be conventionally installed in a corresponding wheel of vehicle within or approach very much with it place.Even the in the situation that of large vehicle, can for the space of each break, be also relatively restricted.In addition, vehicular manufacturer are constantly seeking day by day compact break to reduce this space.In design, need to be connected to while using pneumatic system as the annular disk brake in break major impetus source, the different requirements that meet may be complicated especially.In the design of annular disk brake, exist all the time improved space.

General introduction

On the one hand, at this, provide a kind of annular disk brake with central axial line, this break is characterised in that it comprises: a master bracket, and this master bracket is coaxially settled with respect to this central axial line, a rotor disk, this rotor disk with respect to this central axial line coaxial settle and with this master bracket in a kind of slide and the engaging of transfer of torque among, this rotor disk has the first relative side and the second side, a housing, is provided with this master bracket on it, for rotating around this central axial line, at least one first brake shoe, this at least one first brake shoe has towards a surface of the first side of this rotor disk, and this at least one first brake shoe is connected the inside of this housing, at least one second brake shoe, this at least one second brake shoe has towards a surface of the second side of this rotor disk, a brake shoe bearing for axial lead in fact, this brake shoe bearing is coaxially settled with respect to this central axial line, this brake shoe bearing has the first relative side and the second side, and this at least one second brake shoe is connected in the first side of this brake shoe bearing, an actuator assembly being connected on this housing, this actuator assembly comprises a member axially starting, and the arrangement of a transmit force, the arrangement of this transmit force is included in this member axially starting and a first cam interface between an intermediate member, this intermediate member axially starts between member and the second side of this brake shoe bearing at this, this intermediate member is settled and pivotable in a radial plane coaxially with respect to this central axial line, this arrangement is further included in a second cam interface between this intermediate member and the second side of this brake shoe bearing, when this intermediate member pivotable, this brake shoe bearing moves in the axial direction, this is arranged in this axial amplification that has produced an increase power between member and the second side of this brake shoe bearing that starts thus.

On the other hand, at this, provide a kind of method that increases brake pad clamping force in annular disk brake, this annular disk brake comprises a starter and a rotor disk with spin axis, the method is characterized in that it comprises following simultaneous step: the starter by this break produces first power, this first power is to push outside in a parallel direction of the spin axis with this rotor disk and by the member axially starting; Use this first power to produce a moment of torsion, this moment of torsion has a center of rotation, and this center of rotation is consistent with the spin axis of this rotor disk in fact; Use this moment of torsion to produce second power, this second power is in the identical in fact direction of the direction with this first power and in amplitude, is greater than this first power; And by this second power, be clamped in a plurality of brake shoes on the opposite flank of this rotor disk.

These improved different aspects that represent at this will become clear by reading the following detailed description done by reference to the accompanying drawings.

Brief Description Of Drawings

Fig. 1 shows has the isometric view that improves the annular disk brake example outside arranging;

Fig. 2 shows the isometric view of the break inner side in Fig. 1;

Fig. 3 is an amplification isometric view of cutting part open with the break in Fig. 1;

Fig. 4 is a view that is similar to Fig. 1, and it shows some parts that the remaining part with break is separated;

Fig. 5 is an isometric view, and it shows rear portion and their separated corresponding brake shoes of opening of two half-unit of these outside housing parts of break in Fig. 1;

Fig. 6 is an isometric view, and it shows the link of the master bracket, rotor disk, rotor disk support and the rotor disk that use in the break of Fig. 1;

Fig. 7 is an isometric view, and it shows these different parts demonstrated in Figure 6 while being assembled together;

Fig. 8 is the exploded isometric view of the break in Fig. 1;

Fig. 9 is the rear portion of brake shoe bearing that provides in the break in Fig. 1 and the isometric view of the inner sleeve of inner side housing parts;

Figure 10 is an isometric view, and it shows some parts at the break rear portion in Fig. 1;

Figure 11 shows the view of a subset of these parts of Figure 10 from another angle; And

Figure 12 shows the view of a subset of these parts Fig. 8 from another angle.

Describe in detail

Fig. 1 to Fig. 2 shows a kind of example with the annular disk brake 10 of the assembling that improves design example.The break 10 of showing is designed to the front right wheel (not shown) of large vehicle (as truck or bus).Fig. 1 is the outer side view of break 10 and Fig. 2 is its inner side view.Word " outside " and " inner side " refer to the relative position with respect to the longitudinal axis of vehicle center in the context of this article.When vehicle moves forward, this wheel of vehicle is to rotate up in the side turning clockwise for watching the observer in the outside shown in Fig. 1.An arrow with " forward " mark shown in Fig. 1 and some other accompanying drawing is used for representing the sense of rotation of these rotary components of break 10 when vehicle moves forward.This is corresponding to the main sense of rotation of break 10.

Be noted that break that as break 10 one has a front left side that is ready to use in vehicle is by a mirror image of the break shown in being.Break 10 can also be modified on many different types of traffic tool as demonstrated, comprises the traffic tool that are not intended to for highway travelling, as aircraft.In addition, break 10 being used in a machine that is not vehicle is possible equally.For example, this type of machine can have the element of a belt pulley or another rotation, is connected with break 10 on it.The word " vehicle " using in this article or its equivalent word only refer to shown example and not get rid of break 10 is used in other environment.

The break 10 of showing comprises a master bracket 12, is attached with the wheel of vehicle on it.Support 12 connects around a central interior rotating shaft 14 axle journals, this central authorities' rotating shaft with respect to the central axial line R (seeing Fig. 3) of break 10 by coaxial positioning.The spin axis of wheel is consistent with the central axial line R of break 10.

Support 12 has a plurality of axisymmetric construction bolts 16, and these construction bolts are protruding from a radial component 12a of support 12.Ten construction bolts 16 have been shown in shown example.This type of configuration is common for large truck.The screw thread that is noted that these construction bolts 16 is not illustrated.

The support 12 of showing has a bearing bore 18 therein.It is open that this bearing bore 18 is illustrated in outside.The outer openings of bearing bore 18 can be sealed by a cap (not shown), and this cap is attached on a round flange 12b of this outer openings location.This cap can be useful for preventing that dirt or other pollutants from entering bearing bore 18 from this outside.Other arrangements are also possible.

In these parts of the break 10 of showing many be located in a housing within.This housing comprises an outside housing parts 20 and an inner side housing parts 22.In shown example, outside housing parts 20 is encircled is divided into two half-unit 20a, 20b circumferentially.This two half-unit 20a, 20b are used two bolts 24 and tighten together.Same in shown example, rotating shaft 14 is connected to (as illustrated in greater detail in this article afterwards) on the housing parts 22 of inner side, has formed thus an integral part with it.

Outside housing parts 20 is to use a plurality of bolts 26 and be connected on the housing parts 22 of inner side.Outside housing parts 20 has the flange 28 of a plurality of ring circle distribution, and these flanges provide the anchor point for these corresponding bolts 26 towards 22 extensions of inner side housing parts and they in the axial direction.These flanges 28 of outside housing parts 20 are spaced apart from each other and are had a corresponding opening 30 therein.The configuration of this opening has promoted the air circulation in break 10.Multiple variant is possible equally.

When vehicle is kept in motion, the outside housing parts 20 of housing is the parts that do not rotate with support 12 with inner side housing parts 22.Yet in shown example, they are to be connected on vehicle frame or vehicle body by a knuckle 32.Knuckle 32 is bolted on the rear side of inner side housing parts 22.Fig. 2 shows knuckle 32 and a part of bolt 34, provides these bolts to knuckle 32 is connected on the housing parts 22 of inner side.Because the break 10 of the example of showing is for a front steering wheel, so used knuckle 32.For example, when the driver of vehicle makes wheel steering, therefore whole break 10 carries out pivotable with the wheel of vehicle.Other arrangements are possible equally.For example, if break 10 is used in indeflectible environment, indeflectible wheel (as be provided in those wheels of the most vehicle rears) for example, it is upper or be connected on a suspension arm that outside housing parts 20 and inner side housing parts 22 can be directly connected to parts (as a crossbeam).Then, inner side housing parts 22 can be directly connected on a wheel shaft.According to these requirements, also can design other configurations.

In shown example, an actuator assembly 40 has an outside that is as general as annular configuration and is connected to this housing, is to be more particularly connected on the rear side of inner side housing parts 22 with a plurality of bolts 36.Therefore inner side housing parts 22 is positioned between outside housing parts 20 and actuator assembly 40.Actuator assembly 40 also can be connected on housing by different modes.As will be appreciated, and actuator assembly is provided in the design of enclosure interior and compared, actuator assembly 40 is arranged on to the compactedness that can increase break 10 on the inner side of inner side housing parts 22.

Fig. 2 further shows a pressure fluid entrance 42 for actuator assembly 40.The in the situation that of air starter assembly, entrance 42 can be a kind of pneumatic connection of accepting superheated steam (for example air of pressurization), and break 10 is controlled by this entrance.So the power being produced by actuator assembly 40 is to be controlled by the incoming pressure of actuator assembly 40.Also likely use the liquid (for example, the oil of pressurization) of pressurization or with a kind of motor starter, break 10 started.Moreover, at a kind of vehicle that uses air starter assembly (for example, truck) in situation, break 10 can be designed as has a kind of failure safe pattern, when this entrance is not accepted any pressure or accepted insufficient pressure in addition, break 10 is automatically set to a kind of complete or approaching position of braking completely like this.Equally, likely provide a plurality of valves or a plurality of other elements, so that directly at actuator assembly 40 internal control pressure fluids.So this entrance will only be accepted pressure fluid under a relative constant pressure and will control this startup by a remote command within break 10 self.This remote command can be fluid pipe-line (not shown) electric, machinery or that even use another pressurization, and this pipeline is connected with break 10 by another entrance (not shown).

Fig. 3 is the zoomed-in view of the break 10 shown in Fig. 1, and break 10 is shown as to be had one and cut part open.The figure shows support 12 and be how to be installed to be for around rotating shaft 14 rotation at shown example medium-height trestle 12.As can be seen, support 12 comprises a sleeve portion 12c who extends back, and this sleeve portion is connected on its radial component 12a.Within two isolated

bearings

50,52 are positioned in the bearing bore 18 of support 12.The inner race of these

bearings

50,52 is engaged with in rotating shaft 14 and these outer races are bonded on the inside of radial component 12a and the sleeve portion 12c of support 12 accordingly.These

bearings

50,52 are coaxial with the central axial line R of break 10.

Equally in Fig. 3, rotating shaft 14 is connected on a flange 54 of radially settling, and this flange self is connected on the miscellaneous part of inner side housing parts 22 or otherwise becomes one with it.The flange 54 of showing has a plurality of holes 56, and bolt 34 is attached to this housing on knuckle 32 through these holes.

The customized configuration that is noted that in this these

bearings

50,52 in shown example is a kind of in a plurality of possible configurations.For example, some configurations may require bearing bore 18 to be positioned on the outside with respect to the radial component 12a of support 12.The rotating shaft of this configuration will be longer than shown configuration.Many other configurations are possible equally.

The inner side housing parts 22 that Fig. 3 shows shown break 10 comprises an inner circular flange 22a, and this flange has a plurality of holes with these hole 56 contrapositions of flange 54, and rotating shaft 14 is connected on this flange.Some miscellaneous parts shown in Figure 3 have below been described.

Fig. 4 is an isometric view that is similar to Fig. 1.It shows by this two half-unit 20a, the 20b of outside housing parts 20 separated from one another, has manifested thus the rotor disk 60 of break 10.Yet, be noted that the rotor disk 60 of showing is without its support in Fig. 4.This support will be described below.Rotor disk 60 is with respect to central axial line R (Fig. 3) coaxial positioning.Therefore, rotor disk 60 is rotating parts for break 10, and the spin axis of rotor disk 60 is consistent with the central axial line R of break 10.

Fig. 4 further show a plurality of semicircle brake shoes 62 be installed in outside housing parts 20 this two half-unit 20a, 20b after.These brake shoes 62 are clearly shown that in Fig. 5, and this figure is an equidistant decomposition view, shows the 20a of these half, the rear portion of 20b and the brake shoe 62 of their correspondences.Each brake shoe 62 is attached to the 20a of these half, 20b is upper or otherwise form one with these half portions.Although have two semicircle brake shoes 62 (for each half 20a of, 20b) in the example of showing, likely use a single circular brake shoe (not shown), for example provide and contacting that 360 of rotor disk 60 is spent, or likely use more than two semicircle brake shoes.Outside housing parts 20 also can be made by a single piece that is not separated into two half-unit.

These brake shoes 62 can be used a plurality of screws or other dismountable fastening pieces to be connected this enclosure interior, but also can be for good and all attached on this two half-unit 20a, 20b.For example, these brake shoes 62 metal rear side can soldered or for good and all be attached in a corresponding part in the 20a of these half, 20b.In this way, when these brake shoes 62 are worn, can not make these brake shoes 62 with the 20a of these half, 20b is separated replaces them.Half 20a of, the 20b of the housing parts with integrated brake shoe 62 that more than providing, group is new have simplified maintenance and these brake shoes 62 will be all the time in tram within the 20a of these half, 20b.

In shown example, these brake shoes 62 that are connected on the 20a of these half, 20b have a corresponding surperficial 62a, an outer surface 60a of this surface engagement rotor disk 60.An inner surface 60b of rotor disk 60 is engaged by another group semicircle brake shoe 64, these brake shoes 64 be illustrated with Fig. 4 in the remaining part of break 10 be separated.These surperficial 60a, 60b of rotor disk 60 can be processed into be as far as possible radially and tool surface configuration likely and surface treatment.As will be described below, second group of brake shoe 64 is installed on the brake shoe bearing 66 of an axial lead.

When the correspondence surface of these inner side brake shoes 64 64a engages with the inner surface 60b of rotor disk 60, rotor disk 60 is forced to move to more approaching these brake shoes 62 that are positioned on outside.Because they are connected on the housing parts 20 of outside, these brake shoes 62 on outside are fixed in place.Finally, rotor disk 60 is engaged by these

brake shoes

62,64 on both sides.The power increasing on the inner surface 60b make these brake shoes 64 be bonded on rotor disk 60 increased this brake pad clamping force, therefore increased the friction of these

brake shoes

62,64 on the both sides with rotor disk 60.So kinetic energy that produce or that supplied with by vehicle motor is converted into the heat in break 10 from vehicle movement, until vehicle stops completely or until brake pad clamping force be released.Heat in break 10 is finally dissipated among atmosphere.

Fig. 6 is an equidistant decomposition view, it with cross sectional view show rotor disk 60 and in the example of being shown, provide, rotor disk 60 is installed to the rotor disk support 70 on support 12.As mentioned above, the not shown rotor disk support 70 of Fig. 4.Fig. 7 shows these parts of assembled Fig. 6 afterwards.Be noted that half of only having shown rotor disk 60 in Fig. 6 and Fig. 7.

The rotor disk 60 of the example of showing is to make by two parallel annular wall, and these annular wall have formed these relative outer surface 60a, 60b.These walls link together by a plurality of rib 60c axisymmetric and that extend diametrically, and these ribs form a plurality of air passagewayss, for example, as shown in Fig. 6.The air being heated tends to radially outwards overflow and accepts colder air at the radially inner side of rotor disk 60.This inner shape is just applicable to being assemblied on rotor disk support 70.These different pieces of rotor disk 60 can with form each other one.Multiple variant is possible equally.

As mentioned above, rotor disk 60 is in rotational engagement and rotor disk support 70, to allow rotor disk 60 with respect to support 12, to move in the axial direction with support 12.This moving axially has an amplitude, this amplitude compensation outside pad wearing and tearing.When braking force is released, this amplitude also should be enough to make it from these brake shoes 62 that are provided in the housing parts 20 of outside, to leave.Therefore,, when break 10 is not worked, rotor disk 60 should exceedingly not engage these brake shoes 62, to make minimise friction.

The rotor disk support 70 of the example of showing is one and is as general as annular member, and this annular construction member is coaxial with the central axial line R (Fig. 3) of break 10.This rotor disk support 70 has a cylindrical interior that has been equipped with low-friction material and engages around the sleeve portion 12c of support 12.The periphery of rotor disk support 70 is equipped with a plurality of axially extended pins 72, and these pins are settled thereon axisymmetrically.These pins 72 have an outside 72a, and this outside is assemblied in the sleeve pipe 74 of a plurality of correspondences loosely, and these sleeve pipes are backs of the radial component 12a that integrally provides at support 12.In shown example, provide five pins 72 and five sleeve pipes 74.Yet to use different numbers be also possible and likely make the relative position of these pins 72 and sleeve pipe 74 be inverted.

As being clearly shown that in Fig. 6 and Fig. 7, show that these sleeve pipes 74 of example are positioned between the head of two construction bolts 16.Two sleeve pipes 74 by the head of two construction bolts 16 separation.An annular reinforced wall 76 links together these sleeve pipes 74.At least one form with coating or axle bush on their mating face in these pins 72 and sleeve pipe 74 is equipped with a kind of low-friction material.In this way, moving to axial between rotor disk 60 and support 12 can be relatively easy.And then these pins 72 of the example of showing have one at the middle body 72c of certain form, the diameter of this middle body is greater than the diameter of these sleeve pipes 74.These middle bodies 72c plays the effect of stop member.

As shown in Figure 7, rotor disk 60 is connected on its support 70 by screw or the bolt 78 inserting in the tapped hole of these pins inside end 72b of 70.As shown in the figure, these pins 72 are to use a plurality of brackets 80,82 that radially extend and be connected on the remaining part of rotor disk support 70.Fig. 7 also shows can provide a plurality of large openings to promote air circulation between rotor disk support 70 and the inside of rotor disk 60.Multiple variant is possible equally.

Be noted that these pin outer dias of 72 outside 72a with on the 72b of inner side, be not necessary identical.

In use, when the rotation of wheel on being connected to support 12 and break 10 are activated, the clamping force being applied in the every side of rotor disk 60 by these

brake shoes

62,64 tends to make the rotation of rotor disk 60 to slow down, and produces thus a braking torque in the direction contrary with rotation of wheel.This braking torque is transferred to wheel from rotor disk 60 by these axially extended pins 72.Therefore, these pins 72 have been accepted in fact the whole braking torques that produced by break 10.

Exist many other methods, these methods can be designed as for engaging producing rotation between support 12 and rotor disk 60.However, the rotor disk support 70 of showing has the ability of good self centering and can make rotor disk 60 remain in a radial plane.The hysteresis of break 10 can be also very little.

Fig. 8 is the equidistant decomposition view at most parts of the break 10 shown in Fig. 1 to Fig. 3.Yet, the inside that is noted that shown rotor disk 60 from Fig. 6 and demonstrated in Figure 7 slightly different.In Fig. 8, these parts that rotate together with wheel are support 12 and rotor disk 60.Certainly, rotor disk support 70 (not shown in Fig. 8) also rotates with wheel.As mentioned above, the outside housing parts 20 of housing and inner side housing parts 22 are not rotated with support 12.In shown example, they are can use these bolts 34 and be connected on knuckle 32, as shown in Figure 1 to Figure 3.A part of only having shown these bolts 34 in Fig. 8.Actuator assembly 40 is connected the back of inner side housing parts 22, as below illustrated.

As mentioned above, these brake shoes 64 are connected in a side of a brake shoe bearing 66 being directed axially.The brake shoe bearing 66 of the example of showing comprises two

concentric ring element

66a, 66b (Fig. 9), and these ring elements are used four axisymmetric roller supporting unit 68 and are joined together.These brake shoes 64 can be detachably connected on brake shoe bearing 66.Maintenance has been simplified in this dismountable connection because can change when 64 wearing and tearing of these brake shoes without brake shoe bearing 66 is removed from break 10.Therefore, as shown in Figure 4, by making simply the separation from brake shoe bearing 66 of these two brake shoes 64 just can keep in repair in inner side break 10.For example, this can complete by a mobile locking framework or a plurality of bolt (not shown).

As these brake shoes 62 on outside, likely with a single annular stop pad, replace the brake shoe 64 of these two semicircles, or use the brake shoe 64 more than two semicircles.Equally, in some configurations, these brake shoes 64 can be made into integration or are otherwise for good and all fastened thereon with brake shoe bearing 66.

The brake shoe bearing 66 of the example of showing is to carry out axial lead with a plurality of lines of rabbet joint 90, and these lines of rabbet joint are provided among an inner sleeve 92 of inner side housing parts 22.

Fig. 9 has shown the back of brake shoe bearing 66 and inner sleeve 92.The miscellaneous part that is noted that inner side housing parts 22 is omitted.Inner sleeve 92 can be made one or be otherwise connected on it with the miscellaneous part of inner side housing parts 22, or directly axle journal connects or is for good and all connected in knuckle or rotating shaft or axle beam.

On the brake shoe bearing 66 of shown example, there are two groups of different rollers.First group of roller comprises a plurality of rollers 94.Each roller 94 is installed to be for rotating around a corresponding axle 96, and this axle extends diametrically with respect to central axial line R (Fig. 3).These rollers 94 stretch out on the inner side of brake shoe bearing 66.They are bonded among these lines of rabbet joint 90 of inner sleeve 92 loosely.The width of these lines of rabbet joint 90 is slightly larger than the outer dia of these rollers 94.So these rollers 94 can easily move along these lines of rabbet joint 90.

Be noted that and depend on design, these rollers 94 can for example, be substituted by the follower of other kinds (, sliding button or any low friction slip device).

Return referring to Fig. 8, these lines of rabbet joint 90 of the example of showing are deflections slightly with respect to the direction that is parallel to central axial line R (Fig. 3).When vehicle moves forward, these lines of rabbet joint 90 are setovered in the sense of rotation of wheel.As mentioned above, when break 10 is assembled, these rollers 94 on brake shoe bearing 66 inner sides are engaged with among these corresponding lines of rabbet joint 90 of inner sleeve 92.When brake shoe bearing 66 moves and more approaching or during away from rotor disk 60, this provides the axial lead of this brake shoe bearing.The trailing moment that can produce on brake shoe bearing 66 when break 10 is activated is transferred on the housing parts 22 of inner side.

Because these lines of rabbet joint 90 tilt in Fig. 8 in the direction of rotation, the trailing moment being transferred on brake shoe bearing 66 can produce an axial reagency, thereby increases stopping power.Therefore this extra braking force be proportional to the intensity of braking to a certain extent.The angle of these lines of rabbet joint 90 can regulate to prevent that braking force is out of hand according to specific needs.For example, average angle can be lower than 20 degree, as between 10 degree and 20 degree.Other values are possible.And then these lines of rabbet joint 90 can be also crooked, with convenient brake shoe bearing 66 with respect to rotor disk 60, move more approachingly or away from time change this extra braking force.Nonparallel relative wall is provided also likely to these lines of rabbet joint 90.If if when vehicle moves in astern direction, brake or direction that vehicle is making progress on be stopped on a steep hills slope, this is for preventing what reaction meeting from playing a role.

Fig. 8 also shows at the shown intermediate member 100 between brake shoe bearing 66 and the inner side housing parts 22 of break 10 that is located in.Intermediate member 100 is also shown in Figure 10 to Figure 12.Intermediate member 100 has a plurality of ramped surfaces 102 axisymmetric and that tilt in the axial direction.Intermediate member 100 is coaxially settled with respect to central axial line R (Fig. 3).Its radial plane within inner side housing parts 22 and carry out pivotable around its inner sleeve 92.In shown example, between the rear surface of intermediate member 100 and a surface 105 of the bottom of inner side housing parts 22, a plurality of bearings 103 or other low-friction elements are provided, to assist the rotation of intermediate member 100.Intermediate member 100 does not move in the axial direction.

These ramped surfaces 102 of the intermediate member 100 of showing are in the face of the rear side of brake shoe bearing 66.These cam faces 102 are engaged by corresponding roller 104, and these rollers are provided on these roller supporting unit 68 of brake shoe bearing 66.For example, figure 9 illustrates these rollers 104.They can be arranged on the axle 96 identical with roller 92.Other configurations are possible equally.Be noted that these ramped surfaces 102 and the relative position of these rollers 104 are can be inverted.Other variants are possible equally.

Figure 10 is an isometric view, some parts that it shows inner side housing parts 22 and is connected thereto.Figure 11 is similar to a view of Figure 10 and shows the same dorsal part of observing from different perspectives.Figure 12 is the isometric view of all these parts.The housing 44 of the not shown actuator assembly 40 of Figure 11.Figure 10 and Figure 12 show housing 44 and the inner side housing parts 22 of the actuator assembly 40 with Partial Resection section.

Return referring to Fig. 8, the actuator assembly 40 of the example of showing has a kind of annular configuration.It comprises a pneumatic expandable annular starter 46, and this starter is inserted among the housing 44 of actuator assembly 40.Actuator assembly 40 also comprises a member 48 axially starting, and this member is adjacent with expandable annular starter 46.The member 48 axially starting is by coaxial positioning with respect to central axial line R (Fig. 3).So, for example, and the expandable ring being inserted in interior side body 22 to be compared, the diameter of expandable annular starter 46 can be larger.

The member 48 axially starting comprises four cams that axially stretch out 49, and these cams have the cam face 49a of inclination, and these cam faces are around axial startup member 48 configurations in a kind of axisymmetric mode.These cams 49 of the member 48 axially starting engage a corresponding follower, for example, be configured in a roller 108 at the periphery place of intermediate member 100.These rollers 108 have an axle 110, and this axle is radial directed with respect to central axial line R.As being clearly shown that in Figure 12, the opening 112 of a plurality of arcs is configured on the periphery of rear wall of shown inner side housing parts 22 and these cams 49 of the member 48 axially starting extend past a corresponding opening in these openings 112, for engaging these exterior roller 108.

Because these cams 49 are to engage with these rollers 108 of intermediate member 100 and the member 48 that axially starts only moves on an axial direction, when member 48 moves, intermediate member 100 is forced to carry out pivotable around central axial line R.This pivot movement makes these rollers 104 of brake shoe bearing 66 further move up in these ramped surfaces 102.This causes brake shoe bearing 66 towards an axial motion of rotor disk 60.The whole object of the starter mechanism shown in Figure 10 to Figure 12 is inflatable ring will be reduced to a factor ratio and the clamping force of this brake shoe bearing increased to a factor ratio with the power equivalence of this inflatable ring-shaped brake simultaneously to brake shoe bearing 66 axially displaced.Therefore the power amplification factor, producing can be arranged on a numerical value 5 left and right and by revise these start the angles on slope 49 and the angle of these intermediate ramp 102 recently carry out tuning.In addition, due to the customized configuration of shown example, the axial motion of brake shoe bearing 66 makes brake shoe bearing 66 produce a slight pivot movement, and this is equidirectional with the rotation of the wheel of the vehicle of advancing forward.

For example, as the part of actuator assembly 40, provide a return spring arrangement, when declining or being released with convenient braking force, made brake shoe bearing 66 move away rotor disk 60.This return spring arrangement can comprise one or more springs.In Fig. 8, a spring is schematically shown as 120.For example, this or these spring 120 can be connected between brake shoe bearing 66 and inner side housing parts 22.This or these spring 120 can also otherwise be configured and settle and can design many different being configured for brake shoe bearing 66 is moved and returns to its initial position.

In use, the expandable annular starter of expansion actuator assembly 40 is about to axially to start member 48 and pushes outside to.Yet being configured in of the break 10 of showing produces an amplification that increases power between axial startup member 48 and brake shoe bearing 66.This power amplification has increased the braking force in break 10.The arrangement of the transmit force of the break 10 of showing is included in the member 48 of axial startup and this first cam interface between intermediate member 100, and this second cam interface between intermediate member 100 and brake shoe bearing 66.When break 10 is activated, as stepped on brake petal as vehicle driver, so that during mobile vehicle deceleration, by the starter 46 of actuator assembly 40, produce first power.The residing direction of this first power is parallel with the spin axis of rotor disk 60.Use this first power to produce a moment of torsion, the rotating center that this moment of torsion has is in fact consistent with the spin axis of rotor disk 60 simultaneously.Use this moment of torsion to produce second power, the residing direction of this second power is in fact identical with the direction of this first power and is greater than this first power in amplitude simultaneously.This second power is used as braking force, for clamping these brake shoes 62,64 on opposition side 60a, 60b at rotor disk 60.

As can be appreciated, can make a kind of design of break of similar break 10 all compacter than ever.Break 10 can also be configured to provide a kind of stopping power stable, that self increase in braking process.Generally speaking, therefore many aspects of the design of this disk type braker can be improved, this be by by axially movably this group brake shoe be arranged on a directed brake shoe bearing (it is pushed against on this rotor disk by an intermediate member, as shown) on.For example, this arrangement can increase the compactedness of break.

In addition, around the even circumferential ground assignment system dynamic modification of rotor disk 60 working life of these

brake shoes

62,64.

If wish, can provide Yi Ge mechanism (not shown) to compensate the wearing and tearing that these

brake shoes

62,64 cause in time.For example, this type systematic can move the minimum point on intermediate member 100, and these rollers 104 at the place, back of brake shoe bearing 66 can advance in this minimum point when braking force is released.Other configurations are also possible.

Be noted that for break 10 and in the method for this proposition and can make many modifications.For example, in an annular disk brake, can provide more than one rotor disk.In this case, these two rotor disks will be relative to one another in the axial direction movably.These two rotor disks all can engage in rotation with a master bracket of this break.An extra brake shoe bearing (not shown) can be provided between these two rotor disks.Brake shoe bearing will be two-sided and can freely move in the axial direction in the middle of this, but ideally, and it can also be in rotation joint with a fixed structure (as, these housings 20,22 of the break 10 of showing).If wish, this rotor disk can be a solid rotor, and there is no internal cooling channel (these in example as demonstrated).Equally, these contrary surfaces of rotor disk (with or without a plurality of internal cooling channels) can be slotted or be equipped with a plurality of holes to further improve cooling.If use a kind of air starter, this air starter can have the non-circular shape square of fillet (for example with), thereby at needs place, increases surface area and make starter keep compact as far as possible.As mentioned above, shown in and illustrated actuator assembly can be replaced by another kind of starter, this another kind starter can comprise hydraulic fluid or even a kind of motor drive mechanism.Many other variants are also possible.

Claims

1. an annular disk brake (10) with central axial line (R), comprising:

Master bracket (12), described master bracket is settled coaxially with respect to described central axial line (R);

Rotor disk (60), described rotor disk with respect to described central axial line (R), settle coaxially and with described master bracket (12) in slide and the engaging of transfer of torque among, described rotor disk (60) has relative the first side (60a) and the second side (60b);

Housing (20,22), is provided with described master bracket (12) on it, so that described master bracket (12) rotates around described central axial line (R);

At least one first brake shoe (62), described at least one first brake shoe has towards the surface (62a) of first side (60a) of described rotor disk (60), described at least one first brake shoe (62) is connected to the inside of described housing (20,22);

At least one second brake shoe (64), described the second brake shoe has towards the surface (64a) of second side (60b) of described rotor disk (60);

The brake shoe bearing (66) of substantial axial guiding, described brake shoe bearing is settled coaxially with respect to described central axial line (R), described brake shoe bearing (66) has the first relative side and the second side, and described at least one second brake shoe (64) is connected in the first side of described brake shoe bearing (66);

Be connected to the actuator assembly (40) on described housing (20,22), described actuator assembly (40) comprises the member (48) of axial startup; And

Transmit force device, described transmit force device has comprised member (48) in described axial startup and the first cam interface between intermediate member (100), described intermediate member is positioned between the member (48) of described axial startup and the second side of described brake shoe bearing (66), described intermediate member (100) is settle coaxially and in radial plane, carry out pivotable with respect to described central axial line (R), described transmit force device has further comprised the second cam interface between described intermediate member (100) and the second side of described brake shoe bearing (66), when described intermediate member (100) pivotable, described brake shoe bearing (66) axially moves, described transmit force device produces the amplification of increase power between the member (48) of described axial startup and the second side of described brake shoe bearing (66) thus.

2. annular disk brake as claimed in claim 1 (10), wherein, the amplification of described increase power has the ratio from being greater than 1 to 5.

3. annular disk brake as claimed in claim 1 (10), wherein, described the first cam interface comprises cam axisymmetric and that axially stretch out (49), described cam has the cam face engaging with corresponding the first follower (108), in described cam (49) and described the first follower (108) one is that the member (48) in described axial startup is upper, and another in described cam (49) and described the first follower (108) is on described intermediate member (100).

4. annular disk brake as claimed in claim 3 (10), wherein, described the first follower (108) is the first roller of settling circumferentially around the periphery of the member (48) of described intermediate member (100) or described axial startup, and described the first roller (108) is installed as for the axle (110) of radially the settling rotation around correspondence.

5. annular disk brake as claimed in claim 3 (10), wherein, described intermediate member (100) be pivotally mounted on described housing (20,22) within.

6. annular disk brake as claimed in claim 1 (10), wherein, described the second cam interface comprises the ramped surfaces (102) of axisymmetric and axioversion, described ramped surfaces engages with corresponding the second follower (104), one in described ramped surfaces (102) and described the second follower (104) is in the second side of described brake shoe bearing (66), and another in described ramped surfaces (102) and described the second follower (104) is on described intermediate member (100).

7. annular disk brake as claimed in claim 6 (10), wherein, when described intermediate member (100) moves to described brake shoe bearing (66) more to approach described rotor disk (60), described intermediate member (100) rotates in sense of rotation corresponding to the sense of rotation with described support (12).

8. annular disk brake as claimed in claim 6 (10), wherein, described the second follower (104) engaging with described ramped surfaces (102) is the second roller.

9. annular disk brake as claimed in claim 1 (10), wherein, described brake shoe bearing (66) is to use a plurality of lines of rabbet joint (90) to carry out axial lead, the described line of rabbet joint is arranged on and is connected to described housing (20,22) in inner sleeve pipe (92), described sleeve pipe (92) is settled coaxially with respect to described central axial line (R), and the described line of rabbet joint (90) engages with the 3rd corresponding follower (94) being connected on described brake shoe bearing (66).

10. annular disk brake as claimed in claim 9 (10), wherein, these lines of rabbet joint (90) are angularly to settle with respect to the direction parallel with described central axial line (R), when described brake shoe bearing (66) is when described rotor disk (60) is mobile, the described line of rabbet joint (90) causes described brake shoe bearing (66) to carry out pivot movement in the sense of rotation identical with described rotor disk (60).

11. annular disk brakes as claimed in claim 10 (10), wherein, the described line of rabbet joint (90) has average angle with respect to the direction parallel with described central axial line (R), and described average angle is between 10 degree and 20 degree.

12. annular disk brakes as claimed in claim 1 (10), wherein, described rotor disk (60) comprises supporter (70), described supporter is installed around the sleeve pipe (12c) stretching out from described support (12), and described supporter (70) is directed axially in described support (12).

13. annular disk brakes as claimed in claim 1 (10), wherein, described support (12) comprises a plurality of axially extended bolts, the wheel of vehicle can be connected on described bolt.

14. annular disk brakes as claimed in claim 1 (10), wherein, described actuator assembly (40) comprises air starter (46).

15. annular disk brakes as claimed in claim 14 (10), wherein, described air starter has the configuration of annular substantially, and described air starter (46) is located coaxially with respect to described central axial line (R).

16. annular disk brakes as claimed in claim 1 (10), wherein, described housing (20,22) comprises two parts axially settling, links together described two part detachables.

17. annular disk brakes as claimed in claim 16 (10), wherein, described at least one first brake shoe (62) is quantitatively two, described housing (20,22) quilt in described two parts encircles and is divided into circumferentially two half-unit (20a, 20b), among described two half-unit, connected one corresponding in described two the first brake shoes (62).

18. 1 kinds of methods that increase the brake pad clamping force in annular disk brake (10), the rotor disk (60) that described annular disk brake comprises starter (46) and has spin axis, described method is characterised in that it comprises following simultaneous step:

Starter (46) by described break (10) produces the first power, and described the first power is to push outside in the parallel direction of the spin axis with described rotor disk (60) and by the member (48) axially starting;

Use described the first power to produce moment of torsion, described moment of torsion has center of rotation, and described center of rotation is substantially consistent with the spin axis of described rotor disk (60);

Use described moment of torsion to produce the second power, described the second power is in the substantially the same direction of the direction with described the first power and in amplitude, is greater than described the first power; And

By described the second power, be clamped in the brake shoe (62,64) on the relative both sides (60a, 60b) of described rotor disk (60).

19. methods as claimed in claim 18, wherein, compare ratio that described the second power goes out greatly in amplitude for from being greater than 1 to 5 with described the first power.

20. methods as claimed in claim 18, wherein, produce described the second power and comprise the axial reagency of increase, further to increase described the second power, described axial reagency is produced by trailing moment, and described trailing moment produces while being the brake shoe on clamping described rotor disk (60).